Mining machine with stepper mechanism



Sept. 25, 1962 J. A. swANsoN ETAL 3,055,447

MINING MACHINE WITH STEPPER MECHANISM Original Filed July 22. 19 55 9 Sheets-Sheet 1 Q g q; 5 g

Q INVENTORS ATTORNEY Sept. 25, 1962 J. A. SWANSON ETAL 3,055,447

MINING MACHINE WITH STEPPER MECHANISM 9 Sheets-Sheet 2 Original Filed July 22, 1955 INVENTORS P km N6 JAM: ,4. Jmwom 041mm? @F/l/IAM ATTORNEY Se t. 25, 1962 J. A. SWANSON ET AL 3,055,447

MINING MACHINE WITH STEPPER MECHANISM 9 Sheets-5heet 3 Original Filed July 22, 1955 INVENTORS Jam-1s A. firm/wow n Dnzms R GRAHAM W W W ATTORNEY Se t. 25, 1962 J. A. SWANSON ETAL 3,055,447

MINING MACHINE WITH STEPPER MECHANISM 9 Sheets-Sheet 4 Original Filed July 22. 1955 wywwnww uh T .w. m WM n Wfi .4. cu 1 5 R n Mu 5% p 1962 J. A. SWANSON ETAL 3,

MINING MACHINE WITH STEPPER MECHANISM 9 Sheets-Sheet 5 Original Filed July 22, 1955 INVENTORS A'I'TORNEY Se t. 25, 1962 J. A. SWANSON ET AL 3,055,447

MINING MACHINE WITH STEPPER MECHANISM 9 Sheets-Sheet 6 Original Filed July 22, 1955 mxm INVENTORS J/WFJ x4. Jim/m "0 flan/ME 6mm! BY W W ATTORNEY Sept- 25, 1962 J. A. swANsoN ETAL MINING MACHINE WITH STEPPER MECHANISM 9 Sheets-Sheet 8 Original Filed July 22, 1955 LEV/170R POST Sept. 25, 1962 3,055,447

J. A. swANs'oN EFAL MINING MACHINE WITH STEPPER MECHANISM Original Filed July 22, 1955 9 Sheets-Sheet 9 8 u g b, b E a 3 rem ms: M/VE HOME BY- F455 Hz 75.?

INV EN TORS JAMES A .SWANsOA/ #0 DALI/Is E GRAHAM EL EVATOE ATTORNEY United States Patent Ofiice Patented Sept. 25, 1962 3,tl55,td7 NHNENG MACEENE W111i ETEPFER MECHANISM James A. Swanson, Chicago, and Dallas P. Graham, Homewood, 111., assignors, by ruesnc assignments, to Marmon-Herrington Company, Inc, Indianapolis, Ind, a corporation of lndiana Original appiieatlon July 22, 1%5, Ser. No. 523907, now Patent No. 2,906,515, dated Sept. 29, 1959. Divided and this application .ian. 29, 959, Ser. No. 796,717 7 Claims. (Cl. 186

This invention relates to new and useful improvements in mining machines and deals more particularly with machines for recovering coal, or the like, by auger drilling operations. This application is a division of application Serial No. 523,907, file-d July 22, 1955, now Patent No. 2,906,515, issued September 29, 1959.

An important object of the invention is to provide an anger mining machine equipped with means for effecting movement thereof in the desired direction to position the machine for successive drilling operations.

Additional objects of the invention are to provide a mining machine having a main frame which is of sectic-rial construction for ease in transportation and maintenance; for moving the machine to successive operating positions, and for raising and lowering the machine.

Other objects and advantages of the invention will be apparent during the course of the following description.

In the accompanying drawings forming a part of this specification and in which like reference characters are employed to designate like parts throughout the same,

FIGURE 1 is a top plan view of a machine embodying the invention,

FIGURE 2 is a side elevational View of the machine illustrated in FIG. 1,

FIGURE 3 is a rear end elevational view of the machine of FIG. 1,

FIGURE 4 is a front end elevational view of the ma.- ch-ine of FIG. 1,

FIGURE '5 is a fragmentary elevational view, partly broken away, taken from the side of the machine opposite illustrated in FIG. 2,

FIGURE 6 is a fragmentary top plan view, partly broken away, of the drive end portion of the machine,

FIGURE 7 is a vertical sectional view of one of the elevator posts positioned at each of the four corners of the machine frame,

FIGURE 8 is a fragmentary sectional View taken on line 88 of FIG. 7,

FIGURE 9 is a longitudinal, vertical sectional view of the check valve positioned on the cap of the elevator post of FIG. 7,

FIGURE 10 is a top plan view of one of the sliding shoes employed for moving the machine of FIG. 1,

FIGURE 11 is a vertical sectional view taken on line 11-41 of FIG. 10,

FIGURE 12 is a fragmentary, vertical sectional view taken on line ll-12 of FIG. 11, land FlGUR-E 13 is a diagrammatic View of the hydraulic system of the machine.

In the drawings, wherein, for the purpose of illustration is shown the preferred embodiment of this invention, and first particularly referring to FIGS. 1 to 6, inclusive, there is shown a mining machine, the various component parts of which are mounted on a frame designated in its entirety by the reference character '18. This trarne comprises a plurality of :subassemblies which are separately fabricated to facilitate movement from one location to another and which are so constructed that the entire frame can be easily and quickly assembled at any location at which the machine is to be used.

Considering first the rectangular base or bottom pcrtion of the frame 18, it is assembled from an outer or drive end section 19 extending transversely across the outer end of the frame, as viewed in FIG. 1, and from left-hand and righthand sections 21 and 22, respectively, which extend longitudinally of the frame, as illustrated at the top and bottom, respectively, of FIG. 1. The ad jacent sides of the left hand land right-hand sections 21 and 22 are formed of channels 23, as illustrated in FIG. 4, which are rigidly connected to each other by bolts 24, as is best illustrated in FIG. 6. The outer sides of the two sections 21 and 22 are formed of tubular members 25 which are rigidly connected to the channels 23 by a plurality of transversely extending tubular members 26. The inner ends of the left-hand and right-hand sections 21 and 22, which are adjacent the drive section 19, are formed of angle members 27 which extend between and are rigidly connected to the channels 23 and the tubular members 25 :at opposite sides of each section. The opposite ends of the tubular members 25 at the outer sides of the sections 21 and 22 are inclined angularly upwardly vand are each provided with a mounting pad 28 for a purpose that will be later described.

The drive section 19 is formed with an angle member 29 at its inner side for connection to the angle members 27 by bolts 31, as illustrated in FIG. 6. The ends and outer side of the drive section 19 are formed of tubular members 32 and 33, respectively, which are inclined upwardly at the corners of the heme and are provided with mounting pads 34 for a purpose that will be later described. Extend-ing longitudinally of the drive end section 19 and transversely of the frame '18 are two spaced tubular members 35 which are rigidly connected at their ends to the tubular members 32 and to the adjacent angle member 29 or tubular member 33 by a plurality of laterally extending tubular members 36. An inverted channel member 3'7 overlies the space between and is rigidly connected to the tubular members 35.

At the opposite end of the frame 18 from the drive end section 19, the channel members 23 of the left-hand and right-hand sections 21 and 22 are rigidly connected to an end piece or sill 38 which is formed of an inverted channel member having its opposite end portions inclined on- -gularly upwardly and provided with mounting pads 39. As best illustrated FIG. 4, the depth of the channel member from which the sill 38 is formed is increased at the middle portion 4 1 of the sill for a purpose that will be later described.

At each corner of the frame 18 there is provided a vertically arranged elevator post 42, the structure and op eration of which will be later described. 'It will be noted, however, that the lower end portions of the elevator posts 42 are connected to the mounting pads 34 of the drive end section 19 and to the mounting pads 28 and 39 of the left-hand and right-hand sections 21 and 22 and the sill 38, respectively, in such a manner that the lower end of each elevator post is retractable to a position above the bottom level of the frame L13.

The upper end portions of the elevator posts 42 at the right-hand side of the frame 18 are rigidly connected to each other by a truss 43 which extends longitudinally between the two elevator posts and is provided with structurally reinforced mounting brackets 44 for connection to the elevator posts. The middle portion of the truss 43 consists of a single tubular member 4-5 so that the right side. of the frame 18- is substantially open and unobstructed.

The elevator posts 42 at the left-hand side of the frame 18 have their upper end portions connected by a truss 46 formed of vertically spaced tubular members 47 which are connected by angularly arranged struts 48 and are provided with mounting pads 49 at their end portions for connection to the posts 42.

A truss 51 extends laterally between and is rigidly connected to the elevator posts 42 at each end of the frame 18, each truss 51 being formed of a pair of vertically spaced tubular members 52 connected by angularly arranged struts 53 and provided with mounting pads 54 at their opposite end portions for connection to the post 42. The trusses 51 at opposite ends of the frame 18 are connected to the side trusses 43 and 46 at each corner of the frame by corner braces 55 which extend angularly between the trusses.

The above described structure of the frame 18 provides a strong and rigid support for the operating components of the machine. Further, mobility is provided for the machine by the elevator posts 42 at the corners of the frame 18, which are employed to raise and lower the frame, and by sliding shoes 56 mounted at laterally spaced points on the bottom of the drive portion 19 and at the middle portion 41 of the sill 38. The sliding shoes 56 are employed for moving the frame 18 in any desired direction along the surface on which the machine is to be operated.

Referring now to FIGS. 7, 8 and 9 for a detail description of one of the four identical elevator posts 42, it will be noted that an inner housing member 57 is telescopically arranged within the outer housing member 58, the latter being rigidly connected to the frame 18 as previously described. A cap 59 is mounted on the upper end of the outer housing member 58 by means of screws 61 and a cap 62 is mounted on the lower end of the inner housing member 57 by means of screws 63. The lower end portion of the outer housing member 58 is internally rabbeted to receive a bearing sleeve 64 which engages the outer surface of the inner housing member 57 and is held in place by a snap ring 65. At the upper end portion of the inner housing member 57, a similar bearing sleeve 66 is positioned around the inner housing member in bearing engagement with the bore of the outer housing member 58. The bearing sleeve 66 is held against a shoulder 67 by a snap ring 68. Engagement between the bearing sleeve 64 and the outer surface of the inner housing member 57 and between the bearing sleeve 66 and the bore of the outer housing member 58 will limit relative movement between the two housing members to axial directions.

Mounted on the bottom surface of the cap 62 at the lower end of the elevator post 42 is a spherical knob or ball 69 which is seated in a parti-spherical socket 71 formed in the cleated foot 72. The ball 69 is held in engagement with the socket 71 by means of a clamping ring 73 which is connected to the foot 72 by screws 74. It will be readily apparent, therefore, that the foot 72 may partake of universal movement on the ball 69 to insure proper engagement between the foot and the surface against which it bears.

Mounted within the bore of the inner housing member 57 is a double acting fluid motor designated in its entirety by the reference character 75. The cylinder 76 of the fluid motor 75 has a closed end portion connected to the inner side of the cap 62 of the inner housing mem ber 57 for limited universal movement by means of the right angularly arranged pin 77 and bushing 78 which are carried, respectively, by the cap and cylinder. Extending axially through the opposite end of the cylinder 76 is a tubular plunger 79 having its inner end portion connected within the cylinder to a piston 81 which is provided with seals 82 to collectively prevent the flow of fluid in either direction between the piston and the bore of the cylinder. A seal 83 prevents the leakage of fluid between the outer surface of the plunger '79 and the inner end of the cylinder 76. The outer end portion of the plunger 79 is seated in a recess formed by the annular flange 84 on the inner side of the cap 59 of the outer housing member 58. A gasket 85 is positioned between the outer end face of the plunger 79 and the opposed face of the cap 59. The plunger is rigidly connected to the cap by screws 86, as illustrated in FIG. 12. A passageway 87 through the end cap 59 communicates with the interior of the plunger 79 through the aligned passageway 88 in the outer end of the plunger 79. At the inner end of the plunger 79, ports 89 connect the interior of the plunger and the space between the piston 81 and the end of the cylinder 76 through which the plunger moves. A second passageway 91 in the end cap 59 is aligned with the open end of a conduit 92 which extends longitudinally through the plunger 79 for communication with the space between the piston 81 and the closed end of the cylinder 76.

It will be readily apparent that the admission of pressure fluid through the aligned passageways 87 and 88 into the interior of the plunger 79 and through the ports 89 into the space between the piston 81 and the end wall of the cylinder 76 through which the plunger extends will cause the cylinder 76 to move upwardly along the plunger and will shorten or retract the elevator post 42. Of course, fluid must concurrently be released from the space between the opposite side of the piston 81 and the closed end of the cylinder 76 through the conduit 92 and the passageway 91. To lengthen or extend the elevator post 42, pressure fluid must be admitted through the passageway 91 and conduit 92 into the space between the piston 81 and the closed end of the cylinder 76 and the fluid on the opposite side of the piston must concurrently be released through the ports 89, the interior of the plunger 79 and the aligned passageways 88 and 87. In order to maintain the elevator post 42 at a fixed length, pressure fluid must be neither admitted to nor released from either of the passageways 87 or 91 in the end cap 59.

In order to positively prevent any unintended movement of the fluid motor 75, in the event of a possible failure of the source of pressure fluid or of the hydraulic lines through which pressure fluid flows from the source to the elevator post 42, a double acting check valve 93 is provided for each elevator post.

As illustrated in FIGS. 8 and 9, the valve 93 is positioned on the cap 59 with a gasket 94 therebetween and is clamped to the cap by means :of screws 95 which pass through mounting feet 96 of the valve body 97. The valve body 97 has formed therein a cylindrical bore 98 with two axially spaced internal grooves 99 at the center portion thereof, Radial passageways 101 extend outwardly from each groove 99 for communication with the passageways 87 and 91 in the cap 59 through openings in the gasket 94. Fitted into the bore 98 is a sleeve 102 having radial passageways 103 therethrough for communication with the grooves 99. Positioned centrally within the bore of the sleeve 102 is an annular valve seat 104 having its opposite end portions externally chamfered at 105 to provide clearance between the valve seat and the radial openings 103 in the sleeve. A seal ring 106 is positioned between the seat 104 and the sleeve 102 adjacent each chamfered end portion of the seat for sealing engagement with oppositely arranged valve members 107, as will be later described. Operating plunger 108 is fitted into the bore of the seat 104 and is provided with slots 109 in the opposite end portions thereof for a purpose that will be later described. The valve seat 104 is held in a fixed position in the sleeve 102 by a retaining dowel 111 which is pressed through openings in the valve body 97 and sleeve 102 into an aligned notch in the valve seat. The dowel 111 is internally threaded at 112 to facilitate removal thereof.

Each of the valve members 107 is provided with an internally tapered seating surface 113 for engagement with its associated seal ring 106 and :a seal ring 114 extends circumferentially around the valve member for sealing engagement with the bore of the sleeve 102 to prevent the leakage of fluid therebetween. A spring seat 115 is fitted into each end portion of the bore of the sleeve 102 and a spring 116 is compressed between each spring 1 seat and the adjacent valve member 107 to urge the latter into a position at which its seating surface 113 is in sealing engagement with its associated seal ring 106. The spring seats 115 are held in the bore of the sleeve 102 by the caps 117 which are secured to the opposite ends of the valve body 97. The cap 117 at each end of the valve body 97 is provided with a tapped opening or port 118 in open communication with the adjacent end of the plunger 108 through axial openings in the spring seat 115 and the valve member 107 which are positioned be tween the cap and the plunger.

The operation of the valve 93 will be described in detail as follows:

When no pressure fluid is being admitted to the port 118 at either end of the valve body 97, the springs 116 will urge their associated valve members 7 into positions at which their tapered seating surfaces 113 will engage the associated sealing rings 106. At this time, no fluid can flow in either direction through the radial ports 103 in the sleeve 102 or through the grooves 99 and .passageways 101 in the valve body 97. When, however, fluid is admitted under premure to either of the ports 118, the pressure of the fluid will be applied to the adjacent valve member 107 and will act over substantially the entire area of the end of the valve member adjacent the valve seat 104 to cause the valve member to move axially outwardly away from its seated position against the seal ring 106. The pressure of the fluid entering through the selected port 118 will also act on the exposed end area of the plunger 108 to cause the latter to move axially away from the port to engage and move the valve member 107 at the opposite side of the annular valve seat 104. This movement of the plunger 108 will cause the valve member 107 which it engages to move away from its seated position at which time the radial ports 103 in the sleeve 102 are in open communication with their respective ports 118 at opposite ends of the valve body 97. The pressure fluid is thereby permit-ted to flow through the spring seat 115 and valve member 107 adjacent the port through which the fluid is admitted and through the associated radial ports 103 into one of the passageways 101. The fluid in the other passageway 101, on the other hand, will flow into the valve body 97 through its associated radial ports 10 3 and through the slotted end of the plunger 108, the valve member 107, and the spring seat 115 to the port 1118 at the opposite end of the body from that port to which pressure fluid is being introduced.

The sliding shoe 56 mounted on the middle portion 41 of the sill 38 and the two sliding shoes 56 mounted at spaced points along the channel 37 of the drive section 19 are of identical construction and are best illustrated in FIGS. 10, 11 and 12.

Referring now to these figures for a detail description of one of the sliding shoes 56 and the structure by means of which the shoe is mounted for relative movement on the frame 18, it will be noted that the cylinder 119 of a double acting fluid motor 121 is vertically positioned above an opening 122 in the channel 37 or the channel from which the sill 38 is formed, as the case may be, and is rigidly connected to the channel by screws 123. The upper end of the cylinder 119 is closed except for a threaded port 124 to which is connected a conduit 125 for admitting pressure fluid to the upper end of the cylinder. A piston 126 is mounted in the cylinder 119 and is provided with sealing members 127 for engaging the bore of the cylinder to collectively prevent the leakage of pressure fluid in either direction past the piston.

Connected to the piston 126 and extending downwardly therefrom is an operating plunger 128 which extends through an opening in the lower end wall of the cylinder 119 and through the opening 122 above which the cylinder is mounted. A seal member 129 is carried by the lower end wall of the cylinder 1 19 for sealing engagement with the outer surface of the plunger 128 to prevent the leak- '6 age of fluid from the cylinder. A threaded port 131 is provided adjacent the lower end of the cylinder 119 for connection with a conduit 132 through which pressure fluid may be admitted to the lower end of the cylinder.

At its lower end portion the operating plunger 128 is pivotally connected to a horizontally arranged bearing plate bracket 133 by a pin 134 which extends through the plunger and through aligned openings in the lugs 135 mounted on the spaced vertical side plates 136 of the bracket 133. The bottom plate 137 of the bracket 133 projects laterally outwardly beyond the side plates 136 and a bearing plate 138 is mounted on the lower face of the bottom plate 137. At one end of the bracket 133 there is provided a mounting lug 139 which is positioned between and connected by the pin 140 to the spaced lugs 1 41 of a mounting bracket 142 fastened to the closed end of the cylinder 143 of a conventional, double acting fluid motor 144.

The sliding shoe 56 is channeled to receive the bearing plate bracket 133 and is provided with inwardly extending flanges 145 on its spaced walls 146 which overlie the laterally projecting portions of the bottom plate 137 for engagement therewith to support the sliding shoe when the latter is moved to an elevated position. When the sliding shoe 56 is lowered into engagement with the surface along which the frame 18 is to be moved, the bottom plate 147 of the shoe slidably engages the bearing plate 138 on the bottom of the bracket 133.

At the end of the sliding shoe 56 opposite the lug 139, there is provided a mounting lug 148 for receiving the pin 149 to connect the mounting lug to a clevis 151 at the outer end of the operating plunger 152 of the fluid motor 144. Reciprocating movements of the plunger 152, therefore, will cause relative movement between the shoe and the bearing plate bracket 133.

The operation of the sliding shoes 56 will be described in detail as follows:

With the frame 18 supported by the elevator posts 42 in a raised position, pressure fluid is admitted through the conduits 125 to each fluid motor 121 to lower its piston 126 and plunger 128 to a position at which the attached bearing plate bracket 133 is below the sides of the channel upon which the cylinder 119 is mounted. The bearing plate brackets 133 and their associated sliding shoes 56 can thereupon be pivoted by rotation of the plungers 128 to align the longitudinal axes of the fluid motors 144 with the desired direction of movement of the frame 18. The fluid motors 144 are then actuated to extend the sliding shoes 56 on their hearing plate brackets 133 in the direction in which the frame 18 is to be moved and the frame is thereafter lowered by actuation of the elevator posts 42 to effect engagement between the sliding shoes and the surface along which the frame is to be moved. After the elevator posts 42 are retracted, the fluid motors 144 are then actuated in the opposite directions, whereupon the bearing plate brackets 133 will move longitudinally along their shoes 56 to effect movement of the frame 18 in the desired direction.

After the frame 18 has been thus moved, it is again raised by the elevator posts 42 to lift the sliding shoes 56 out of contact with the supporting surface and the fluid motors 144 are actuated to effect movement of the shoes in the proper direction relative to the frame so that, when the shoes are again lowered into engagement with the supporting surface, proper actuation of the motor 144 will again effect the desired movement of the frame. When the frame 18 has been positioned in the desired location by successive movements as described above, the bearing plate bracket 133 of each shoe 56 is aligned with its associated channel member and its fluid motor 121 is actuated by the admission of pressure fluid through the conduit 132 to lift the bracket and its attached sliding shoe into a retracted position within he supporing channel member.

Referring once again to FIGS. 1 to 6, inclusive, for a detail description of the power plant employed for operating the machine, an internal combustion engine 153 is mounted on the drive end section 19 of the frame, the engine being supported on pedestals 154, as best illustrated in FIG. 6, and a pedestal 155, as best illustrated in FIGS. 2 and 3. At the power output end of the engine 153 its drive shaft is connected to a power take off assembly, including a clutch, within the housing 156, a twin hydraulic coupling 157 of traction design, a universal joint 158, and a bevel gear transmission unit 159. The bevel gear transmission unit 159 is mounted on a pedestal 160 that is rigidly connected to the frame 18 and is provided with a gear shifting mechanism 161 by means of which the direction of rotation of the power output shaft 162 may be reversed or stopped while the engine 153 continues to operate.

At the fan end of the engine 153, its drive shaft is extended past the fan pulley 163 and is drivingly connected to the driven shaft 164 of a Vickers double pump 165 which is of conventional vane type construction and is mounted on a bracket 166 carried by the pedestal 155. The inlet port of the double pump 165 is connected through a filter 167 to a hydraulic tank 168 which is supported on the angle 29 and channel 37 of the drive end section 19 adjacent the right-hand side of the frame 18. The two outlet ports of the double pump 165 supply the pressure fluid for operating all of the fluid motors of the machine and are connected into the hydraulic circuit of the machine in a manner which will be later described.

Mounted on the drive end section 19 of the frame 18 between the angle 29 and channel 37 and inwardly of the hydraulic tank 168 is a fuel tank 169 for the engine 153. The batteries for the engine 153 are carried on brackets 171 that are rigidly mounted on the tubular member 33 at the outer side of the drive end section 19. As is best illustrated in FIGS. 1 and 2, a catwalk 172 is mounted on the frame 18 in overlying relationship with the tanks 168 and 169. Another catwalk 173 is suitably mounted to extend longitudinally along the outer side of the right-hand section 22 of the frame 18 and additional catwalks 174, 175 and 176 extend transversely across the right-hand section and are supported on angles 178 which extend longitudinally between the transverse tubular members 26.

Mounted on and extending longitudinally along the inner and outer sides of the left-hand section 21 of the frame 18 and into overlying relationship with the adjacent portions of the drive end section 19 are two track assemblies 179 and 181 respectively.

As best illustrated in FIGS. 4 to 6, inclusive, the track assembly 179 is formed with an inwardly projecting top flange 182 and with an angle member 183 rigidly mounted in spaced relationship below the top flange to provide a horizontal surface spaced downwardly from the top flange and a vertical surface extending downwardly from the inner edge of the horizontal surface. As illustrated in FIG. 4, the track 181 at the inner side of the left-hand section 21 is also formed with an inwardly projecting top flange 184 and with an angle member 185 rigidly mounted in spaced relationship below the top flange to provide a horizontal surface spaced downwardly from the bottom surface of the top flange and a vertical surface projecting downwardly from the inner edge of the horizontal surface. The inner track assembly 181 is also provided with a catwalk 186 which is suitably mounted on the top of the track assembly and extends longitudinally along the inner side of the left-hand section 21.

Mounted for longitudinal movement along the track assemblies 179 and 181 is a carriage 187 having pairs of right angularly arranged rollers 188 and 189 at each corner thereof for engaging the vertical and horizontal surfaces, respectively, of the angle members 183 and 185 to facilitate and guide the movement of the carriage. Mounted on the carriage 187 is a power transmission unit 191 which is described in detail in Patent No. 2,906,515.

As is best illustrated in FIG. 5, the transmission unit 191 is so positioned on the carriage 187 that the drive bar 272 is axially aligned with the output shaft 162 of the bevel gear transmission unit 159. One end of the drive bar 272 is connected to the output shaft 162 by a flexible coupling 273 and the opposite end of the drive bar is connected to the longitudinally aligned elevator post 42 by means of a bearing support 274 which permits free rotation of the bar.

As is best illustrated in FIGS. 5 and 6, the carriage 187 and the transmission unit 191 mounted thereon are moved longitudinally of the frame 18 by a drive chain 275, positioned adjacent the track 181, and a drive chain 276, positioned at the left side of the frame. The ends of the chain 275 are connected to opposite sides of the carriage 187 and the chain is trained around an idler sprocket 277 mounted on the sill 38 and a drive sprocket 278 mounted on the tubuular members 36 of the drive end section 19 of the frame. The shaft 279 of the drive sprocket 278 is supported for rotation by a bearing 281 and is connected through universal joints 282 and a torque tube 283 to a conventional worm gear drive 284.

The ends of the chain 276 are connected to ears 285 of a bracket 286 which is mounted on the top of the transmission unit 191 in longitudinal alignment with the elevator posts 42 at the left side of the frame 18 and the chain is trained around an idler sprocket 287, mounted on the elevator post 42 at the forward end of the frame, and a drive sprocket 288, mounted on a shaft 289 carried by a bracket 291 on the elevator post 42 at the drive end of the frame. Mounted in axially spaced relation with the drive sprocket 288 on the shaft 289 is a second sprocket 292 which is connected by a drive chain 293 to a drive sprocket 294 on the output shaft of the Worm gear drive 284. The worm gear drive 284 is powered by a conventional, vane type rotary fluid motor 295 which is mounted directly on the housing of the Worm gear drive.

It will be readily apparent that actuation of the fluid motor 295 to eifect rotation of the worm gear drive 284 will effect synchronized rotation of the two drive sprockets 278 and 288 for the chains 275 and 276, respectively. The chains 275 and 276 are thereby moved to elfeet movement of the carriage 187 along its supporting tracks 181 and 182. The fluid motor 295 is, of course, reversible so that the direction of movement of the carriage 187 may be reversed when the carriage has been moved to either end of its path of travel. The manner in which the fluid motor 295 is supplied with pressure fluid to control the periods and direction of operation of the motor will be fully described in connection with the complete hydraulic system of the machine.

Referring now to FIGS. 1, 4 and 6 for a detail description of the support rollers 296 mounted on the outer end portion of the left-hand section 21 of the frame 18, it will be noted that each roller extends longitudinally between and is rotatably mounted on the free end portions of a pair of pivot arms 297. The arms 297 of each pair are pivotally supported at the middle portion of the transverse tubular members 26 of the left-hand section 21 of the frame 18 by pins 298 so that pivotal movement of the arms will cause the rollers 296 to move toward and away from the projected axis of the chuck 219. Connected between the free end of each pivot arm 297 and the adjacent side member 23 or 25 of the lefhand section 21 of the frame 18 is a conventional reciprocating type fluid motor 299. All of the motors 299 are connected to a common source of pressure fluid so that actuation of the motors will effect simultaneous movement of the rollers 296 upwardly and inwardly toward the projected axis of the chuck 219. The release of pressure fluid from the motors 299, on the other hand, will permit the weight of the rollers 296 to return the pivot arms 297 to their retracted positions, as illustrated in FIG. 4. It will be noted, that when the pivot arms 297 and rollers 296 are in their retracted positions, sutficient clearance is provided for movement of the carriage 187 into overlying relationship with the arms and rollers. The manner in which the supply of pressure fluid to the motors 299 is controlled will be fully described at a later point in connection with the complete hydraulic system of the machine.

As is best illustrated in'PlIGS. l and 2, a worm gear drive 301 is mounted on the drive end portion 19 of the frame 18 between the hydraulic tank 168 and the fuel tank 169 and beneath the catwalk 172. The worm gear drive 301 is powered by a conventional vane type rotary fiuid motor 302 the operation of which will be later described in connection with the hydraulic system for the complete machine. Mounted on the output shaft of the worm gear drive 301 is a drum 303 for receiving a cable 304 which extends upwardly from the drum and is trained laterally over a pulley 305 carried by the bracket 306 above the top surface of the catwalk 172. From the pulley 305, the cable 304 extends laterally to a pulley 307 which is rotatable about a vertically arranged pin 308 to guide the movement of the cable longitudinally of the frame 18. The pin 308 is selectively positioned in laterally spaced holes 309 in the bracket 306 to permit lateral adjustment of the point of support for the cable 304 provided by the pulley 307. A hook 311 is mounted on the end of the cable 304 for a purpose that will be later described.

Extending longitudinally of the right-hand section 22 of the frame 18 from the drive end section 19 to the sill 38 is a shallow pan 312 which rests upon and is supported by the transverse catwalks 174, 175 and 176. The pan 312 is mounted on catwalks 174, 175 and 176 by parts, not shown, which cooperate with laterally spaced holes 313 in the catwalks' so that the position of the pan can be laterally adjusted into substantial alignment with the support provided by the pulley 307 for the cable 304. At the end portion of the pan 312 adjacent the sill 38, a ramp 314 extends downwardly and outwardly from the sill.

It will be readily apparent, that when the fluid motor 302 is operated in a direction to play out the cable 304, the hook 311 may be drawn longitudinally of the frame above the pan 312 for connection to a drilling implement such as the auger section 315 as illustrated by broken lines in FIG. 2. Operation of the motor 302 in the opposite direction will thereafter cause the auger section 315 to be drawn longitudinally onto the pan 312 to the position illustrated in full lines in FIGS. 1 and 2. The ramp 314 facilitates this movement of the auger section 315 onto the pan 312.

Referring now to FIGS. 1 to 4,- inclusive, for a detaildescription of the mechanism for transferring the auger sections from the position occupied by the auger section 315 laterally across the frame 18 to the position occupied by the auger section 316 of FIG. 1 or from a position adjacent the right-hand side of the frame to either of the positions occupied by auger sections 315 and 316, there is suspended from the tubular member 45 of the truss 43 and from a plate 317 extending vertically between the members 47 of the truss 46 and I-beam 318 which extends laterally across the frame and projects outwardly from the right-hand side of the frame. Mounted on the top of the outwardly projecting end portion of the beam 318 is a worm gear drive 319 which is powered by a conventional vane type rotary fluid motor 321 and has mounted on its output shaft a drum 322. The periods and direction of operation of the fluid motor 321 will be fully described in connection with the complete hydraulic system of the machine.

Mounted on the projecting end of the beam 318 is a pulley 3'23 and a hoist carriage 324 is suspended for longitudinal movement along the beam by wheels 325 which are mounted on stub axles 326 projecting inwardly from the sides of the carriage. A pair of pulleys 327 are mounted on the hoist carriage 324 in longitudinally spaced relationship below the beam 318. Wound onto the drum 322 is a cable 328 which is trained around the pulley 323 at the end of the beam 318 and is anchored to the truss 46 at the opposite side of the frame 18. Between the pulleys 327, the cable 328 is formed into a depending loop which passes around a pulley 329 of a block 3 31 to support the latter for vertical movement in accordance with the length of the depending loop. In other words, as the cable 328 is wound onto and off of the drum 322, the length of the depending loop between the pulleys 327 will be decreased and increased, respectively, to vary the height of the block 331. On the other hand, the drum 322 may be held in a fixed position while the hoist carriage 324 is moved laterally across the frame and the block 331 will remain at a given elevation during this later-a1 movement of the carriage. Mounted on the block 331 is a hook 332 having a handle 333 formed thereon to facilitate insertion of the hook into holes 334 near the longitudinal midpoint of an auger section, as illustrated in FIG. 2.

It will be readily apparent that the hoist carriage 324 may be moved longitudinally along the beam 318 to a position above an anger section on the pan 312, or adjacent the side of the frame 18, and the block 331 thereafter lowered by actuation of the motor 321 to a position at which the hook 332 may be inserted into the hole 334 of the auger section. The direction of operation of the motor 321 is thereafter reversed to shorten the cable 328 and raise the auger section to a level at which the hoist carriage 324 maybe moved laterally across the frame 18 without interference between the auger section and the track assembly 181. The block 331 is then lowered to position the auger section in axial alignment with the chuck 219 and the carriage 187 is advanced to a position at which the auger section may be coupled to the chuck. The supporting rollers 22.6 are thereafter elevated to positions of engagement with the auger section, at which time the hook 332 may be disengaged from the auger section and the hoist carriage 324 moved to the right-hand side of the frame 18.

Referring now to FIG. 13 for a detail description of the hydraulic system incorporated in the machine, it will first be noted that the vane type double pump includes two vane carrying rotors mounted in a single housing on a common drive shaft and receiving their supply of fluidthrough a common inlet port. Separate pressure fluid outlet ports are provided for the two rotors of the pump. The inlet port of the pump 165 is connected to the hydraulic tank 168 by a supply line 335 having the filter 167 mounted therein.

One of the outlet ports of the pump 165 is connected to the inlet manifold p of a Vickers multiple valve unit 336 by a hydraulic line 337. The multiple valve unit 336 includes the inlet manifold p, valve sections a to i, inclusive, and an outlet manifold r all of which are of the type illustrated in United States Patent No. 2,489,435, issued to James Robinson on November 29, 1949. (The second fluid outlet port of the pump 165 is connected to the inlet manifold p of a multiple valve unit 338 by a hydraulic line 339. In addition to the inlet manifold p, the valve unit 338 includes three valve sections j to l, inclusive, and

an outlet manifold r.

The general construction of the various portions of the valve 338 is the same as those of the valve unit 336. The hydraulic line 339 has connected thereto a bypass line 341 having a filter 342 of limited capacity mounted therein. A limited quantity of fluid from the line 339, therefore, is permitted to flow from the line 339 through the bypass line 341 and filter 342 for return to the tank 168.

Considering first the multiple valve unit 336, each of the valve sections a to g, inclusive, and i is provided with two ports which are alternatively connected to the inlet manifold p and the outlet manifold r by movement of a valve plunger in opposite directions from its neutral position. The valve plunger of each section is spring biased into its neutral position and is provided with an operating handle 343, as illustrated in FIGS. 71 to 4, inclusive, for

movement of the plunger in either direction from its neutral position. At the neutral position of the valve plunger, both ports of each valve section are closed and the fluid entering the inlet manifold p flows directly through the valve section to the outlet manifold r. When one of the valve sections is actuated by movement of its plunger out of its neutral position, the full flow of fluid into the inlet manifold p is diverted to the selected port of the valve section, and when more than one of the valve sections have their valve plungers displaced from their neutral positions, the flow of fluid into the inlet manifold is divided between the various actuated valve sections. The inlet manifold p is provided with an integral relief valve to prevent the application of excessive pressure to the various valve sections and with a check valve which prevents back flow from the ports of the valves to the pump.

The valve section It is identical to the other valve sections of the unit 336 except that one of the ports of this section is plugged so that movement of its valve plunger in one direction connects the open port to the inlet manifold p and movement in the opposite direction from its neutral position connects the open port to the outlet rnanifold r. In its neutral position, the plunger of the valve section 11 closes the open port and permits the flow of fluid through the valve section to the outlet manifold r.

The ports of the valve sections, a to d, are connected by pairs of hydraulic lines 344 and 345, 346 and 347, 348 and 349, and 351 and 352, respectively, to the ports of the check valves 93 associated with the elevator posts 42 at the four corners of the frame 18. The ports of the valve section (2 are connected by line 353 and branch lines 125 to one port of each fluid motor 121 of the sliding shoes 56 and by line 354 and branch lines 132 to the other port of each fluid motor 121. The two ports of the valve section 1 are connected respectively by line 355 and branch lines 356 to one port of each fluid motor 144 asso ciated with the sliding shoes 56 carried by the drive end portion 19 of the frame 18, and by line 357 and branch lines 358 to the other port of each of these fluid motors. Valve section g is connected by lines 359 and 361 to the two ports of the fluid motor 144 associated with the sliding shoe 56 carried by the sill 38. The single open port of valve section h is connected by line 362 and branch lines 363 to the four fluid motors 299 associated with the support rollers 296. Valve section i has its two ports connected by hydraulic lines 364 and 365 to the two pressure fluid inlet ports of the rotary type fluid motor 295. The outlet manifold r of the multiple valve unit 336 is connected by a hydraulic line 366 to a return manifold 367 from which fluid flows directly back to the tank 168 through the line 368.

The vane type rotary fluid motor 295 has two pressure fluid inlet ports through which fluid may be alternately admitted to effect rotation of the motor in opposite directions and a single outlet port through which fluid is released to the hydraulic line 369 for return to the manifold 367.

Considering now the multiple valve unit 338, this unit includes three valve sections which are of the same construction as the sections a to g, inclusive, and i of the valve unit 336. Valve section 1' has its two ports connected to the two inlet ports of the vane type rotary fluid motor 321 by hydraulic lines 371 and 372 through which pressure fluid is alternately admitted to effect rotation of the fluid motor in opposite directions. The outlet port of the fluid motor 321 is connected by a hydraulic line 373 to the return manifold 367. The two ports of the valve section k are connected by lines 374 and 375, respectively, to the two inlet ports of the vane type rotary fluid motor 302 for alternately supplying pressure fluid to rotate the motor in opposite directions. The outlet port of the motor 302 is connected by a line 376 to the return manifold 367. The two ports of the valve section I are connected, respectively, by the line 377 to the line 365 and by the line 378 to the line 364. Since the fluid motor 295 is of the positive displacement vane type, it will be readily apparent that the common connections between the outlet ports of the valve sections i and l and the ports of the motor will permit operation of the valve sections jointly or independently to vary the speed of operation of the motor.

Referring now to FIGS. 1 to 4, inclusive, for a detail description of the manner in which the multiple valve untis 336 and 338 are mounted on the frame 18, the control station for the machine is located at the inner end of the catwalk 172 on the drive end section 19 of the frame 18. Extending upwardly from the inner end of the catwalk 172 is a stepped control bracket 379 the upper end portion of which is connected by laterally extending members 381 to the bottom tubular member 47 on the truss 46. The multiple valve unit 336 is mounted on the upper portion of the bracket 379 and the multiple valve unit 338 is mounted on the lower portion of the bracket. The operating handles 343 of the various valve sections of the two multiple valve units 336 and 338 are arranged for operation from the catwalk 172 and suitable instruction plates, not shown, are provided for indicating the function controlled by each handle. The hydraulic lines for connecting the various valve sections to the fluid motors controlled thereby are omitted from FIGS. 1 to 4, inclusive, for purposes of clarity. It will be noted, however, that metallic tubing has been used for all the hydraulic lines of the system which are not subject to movement or to vibration and that all of the hydraulic lines have been mounted, when possible, on the various appropriate portions of the frame 18 to provide a strong and rigid support for the lines.

The operation of the machine will be described as follows, and will start with the assumption that a drilling operation has just been completed and the frame 18 is supported in an elevated position on the elevator posts 42 as illustrated in broken lines in FIG. 3. The fluid motors 121 of all of the sliding shoes 56 are actuated by movement of the operating handle 343 of the valve section e in a direction to cause fluid to flow through the line 353 and the branch lines 125. The sliding shoes 56 will thereupon be lowered to the positions illustrated by broken lines in FIGS. 2 and 4 at which positions the shoes are freely rotatable about vertical axes to permit the axes of their associated fluid motors 144 to be aligned with the desired direction of movement of the frame 18.

When the shoes 56 have been so aligned, the operating handles 343 of valve sections a to a, inclusive, are moved in a direction to permit pressure fluid to flow from the inlet manifold p through the hydraulic lines 344, 346, 348 and 351 and to permit fluid to flow through the valve sections from the hydraulic lines 345, 347, 349 and 352 for return to the tank 168. This flow of pressure fluid through the hydraulic lines 344, 346, 348 and 351 will actuate the check valves 93 of the various elevator posts 42 to open the passageways 87 and 91 in the cap 59 of each elevator post as previously described. The pressure fluid will then flow into the fluid motors 75 through the passageways 88 and will flow from the fluid motors 75 through the conduits 92 and passageways 91 to shorten the elevator posts 42 and lower the frame 18 to a position at which the sliding shoes 56 rest upon the surface along which the machine is to be moved.

As was previously discussed in connection with the description of the sliding shoes 56, the fluid motors 144 associated with the shoes carried by the drive end section 19 and the fluid motor 144 associated with the sliding shoe carried by the sill 38 will have been actuated by the operation of the valve sections 7 and g to extend the sliding shoes in the direction of intended movement of the frame before the shoes engage the surface along which the machine is to be moved. After the shoes 56 have engaged the surface, the valve sections 1'' and g are again operated by their handles 353 to effect relative 13 movement between the shoes and frame in an opposite direction so that the frame is moved on the shoes in the direction in which the axes of the fluid motors 144 have been arranged.

The fluid motors 75 of the various elevator posts 42 are then actuated by operation of the valve sections a to d, inclusive, to cause pressure fluid to flow into the hydraulic lines 345, 347, 349 and 352 and from the lines 344, 346, 348 and 351. The fluid motors 75 will thereupon extend the elevator posts 42 to lift the frame 18 to a position at which the sliding shoes 56 no longer engage the surface below the frame.

The frame 18 may thereafter be moved along the shoes 56, as described above, until the machine has been properly positioned for drilling a hole in laterally spaced parallel relationship with the previously drilled hole. The frame 18, of course, may be moved to an entirely new location bearing no fixed relationship to the previously drilled hole or may be pivoted about the vertical axis of the fluid motor 121 associated with the shoe 56 carried by the sill 38 by operation of the valve section 7 while the valve section g remains in its neutral condition. Normally, however, the frame 18 will be moved laterally along a bench adjacent the wall into which successive parallel holes are to be drilled so that the fluid motors 144 of all of the sliding shoes 56 will be operated concurrently as described above.

It will be appreciated that the frame 18 may be leveled on its supporting surface by independent actuation of the valve sections a to d, inclusive, to individually adjust the lengths of the various elevator posts 42 in accordance with any irregularity in the level of the supporting surface.

Having thus described the invention, we claim:

1. In a mining machine, a frame, means for raising and lowering the frame, means for moving the frame along the surface upon which it rests comprising a plurality of shoes, means for mounting each shoe on the bottom portion of said frame, said shoe mounting means permitting horizontal movement of its shoe relative to said frame to advance the frame over a supporting surface and vertical movement of its shoe relative to the frame to and from a predetermined position below the bottom of the frame to engage and disengage said surface, and a fluid motor associated with each of said shoes for moving the latter in said horizontal direction relative to said frame, said shoe mounting means also permitting its shoe to be rotated about a vertical axis for varying the direction of horizontal movement of the shoe relative to said frame.

2. In a mining machine, a frame, a plurality of sliding shoe mechanisms, separate means for connecting each one of said mechanisms to the frame to permit its mechanism to be bodily .angularly adjusted about a vertical axis so as to arrange the sliding shoe mechanism at any desired angular position relative to the length of said frame to determine the horizontal direction in which the frame may be moved, each of said mechanisms including two elongated, superimposed plate members, bracket means attaching the upper plate member to its aforesaid connecting means, means for longitudinally slidingly attaching the bottom plate member to the upper plate member with the bottom plate member being adapted to engage the surface on which the said frame is supported, means for raising and lowering the frame to move the bottom plate member of each shoe mechanism into and out of engagement with the surface on which the frame is supported and relative to which the frame is to be moved, and means for sliding the upper plate members in one direction relative to the bottom plate members, when the latter members are in engagement with the supporting surface, and for sliding the bottom plate members in the same direction relative to the upper plate members, when the frame is raised to move the bottom plate members out of engagement with the supporting surface.

3. A mining machine as defined in claim 2 further characterized by each one of said connecting means including a device to bodily move its mechanism vertically to and from a predetermined position below the bottom of said frame.

4. A mining machine as defined in claim 3 further characterized by the said device of each connecting means comprising a double acting fluid motor arranged with its axis extending vertically of the frame.

5. A mining machine as defined in claim 2 further characterized by the means for sliding the upper and bottom plate members relative to each other comprising a double acting fluid motor for each mechanism with each fluid motor including a cylinder connected at its outer end to the outer end portion of one of said plate members and a piston in the cylinder having a piston rod connected at its outer end to the opposite outer end portion of the other plate member.

6. A mining machine as defined in claim 2 further characterized by each one of said connecting means including a double acting fluid motor to bodily move its mechanism vertically to and from a predetermined position below the bottom of said frame, and the means for sliding the upper and bottom plate members relative to each other comprising a double acting fluid motor for each mechanism with each fluid motor comprising a cylinder connected at its outer end to the outer end portion of one of said plate members and a piston movable in the cylinder and having a piston rod connected at its outer end to the opposite outer end portion of the other plate member.

7. A mining machine as defined in claim 6 further characterized by said frame carrying a source of supply of compressed air, a series of valves mounted on the frame and each having an inlet port connected to the source of supply of compressed air and two outlet ports, the two outlet ports of one of said valves having connection lines extending to the opposite end portions of all of the double acting fluid motors included in the connecting means for the sliding shoe mechanisms, the two outlet ports of another of said valves having connecting lines extending to the opposite end portions of the double acting fluid motor which effects relative sliding movement of the upper and bottom plate members of one of said shoe mechanisms, and the two outlet ports of still another one of said valves having connecting lines extending to the opposite end portions of all of the remaining double acting fluid motors which effect relative sliding movement of the plate members of the remaining shoe mechanisms.

References Cited in the file of this patent UNITED STATES PATENTS 2,062,657 Joy Dec. 1, 1936 2,635,585 Damgaard Apr. 21, 1953 2,715,029 Compton Aug. 9, 1955 2,801,094 Ball July 30, 1957 2,935,309 McCarthy May 3, 1960 

